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WO2006008875A1 - Circuit hydraulique pour véhicule de travail - Google Patents

Circuit hydraulique pour véhicule de travail Download PDF

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Publication number
WO2006008875A1
WO2006008875A1 PCT/JP2005/010062 JP2005010062W WO2006008875A1 WO 2006008875 A1 WO2006008875 A1 WO 2006008875A1 JP 2005010062 W JP2005010062 W JP 2005010062W WO 2006008875 A1 WO2006008875 A1 WO 2006008875A1
Authority
WO
WIPO (PCT)
Prior art keywords
flow rate
driving
cooling fan
actuator
hydraulic pump
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2005/010062
Other languages
English (en)
Japanese (ja)
Inventor
Yutaka Sugimoto
Eiji Ishibashi
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Komatsu Ltd
Original Assignee
Komatsu Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Komatsu Ltd filed Critical Komatsu Ltd
Publication of WO2006008875A1 publication Critical patent/WO2006008875A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/162—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for giving priority to particular servomotors or users
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P7/00—Controlling of coolant flow
    • F01P7/02—Controlling of coolant flow the coolant being cooling-air
    • F01P7/04—Controlling of coolant flow the coolant being cooling-air by varying pump speed, e.g. by changing pump-drive gear ratio
    • F01P7/044—Controlling of coolant flow the coolant being cooling-air by varying pump speed, e.g. by changing pump-drive gear ratio using hydraulic drives
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/255—Flow control functions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/62—Cooling or heating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
    • F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6652—Control of the pressure source, e.g. control of the swash plate angle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7058—Rotary output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/78—Control of multiple output members
    • F15B2211/781—Control of multiple output members one or more output members having priority

Definitions

  • the present invention relates to a hydraulic circuit of a work vehicle.
  • Patent Document 1 pressure oil discharged from a fixed displacement hydraulic pump force is divided by a flow control valve with pressure compensation, and a part thereof is supplied to a fixed displacement hydraulic motor that drives a cooling fan.
  • a hydraulic circuit that supplies the remaining pressure oil to the work machine is disclosed.
  • the oil discharged from the variable displacement hydraulic pump is related to an engine mounted on a vehicle such as a railway vehicle and a device for driving a cooling fan of the hydraulic device.
  • a fixed capacity hydraulic motor for driving a cooling fan via a diaphragm having a variable diaphragm type diaphragm mechanism.
  • the differential pressure before and after the throttle that is, the discharge amount of the variable displacement hydraulic pump is controlled according to the engine speed, and the opening area of the throttle is controlled according to the cooling water temperature.
  • the rotational speed of the hydraulic motor for driving the fan is kept constant.
  • Patent Document 1 Japanese Patent Application Laid-Open No. 5-24445 (Page 2, Figure 1-2)
  • Patent Document 2 JP-A-9 317465 (Page 3-4, Fig. 1)
  • the present invention has been made paying attention to the above-mentioned problems, and an object of the present invention is to provide a hydraulic circuit for a work vehicle that improves efficiency and is suitable for driving a cooling fan and a work implement. Means for solving the problem
  • the work machine actuator in the hydraulic circuit of the work vehicle, the work machine actuator, the cooling fan drive actuator, the work machine activator, and the cooling fan drive actuator
  • a common variable displacement hydraulic pump that supplies pressure oil and a control device that controls the flow rate of the pressure oil to the working machine actuator and the flow rate of the pressure oil to the cooling fan drive actuator are configured.
  • the maximum discharge amount of the variable displacement hydraulic pump is greater than the flow rate obtained by adding the maximum flow rate required for driving the work machine and the maximum flow rate required for driving the cooling fan. If the discharge amount of the hydraulic pump is insufficient for the flow rate required for driving the work implement and the flow rate required for driving the cooling fan, the control device is necessary for the work implement. Supply the flow rate, and supply the remaining flow rate to the cooling fan drive actuator.
  • the number of pumps can be reduced by using a common pump for supplying pressure oil to the working machine actuator and the cooling fan driving actuator.
  • this pump has a variable displacement type and has a control device that controls the flow rate of the pressure oil to the work machine actuator and the flow rate of the pressure oil to the cooling fan drive actuator so that the required flow rate is always supplied from the pump. Since only the liquid is discharged, the efficiency can be improved.
  • the variable displacement hydraulic pump has a maximum discharge amount that is simply the sum of the maximum flow rate required for driving the conventional work machine and the maximum flow rate required for driving the cooling fan.
  • the size can be reduced, and the manufacturing cost can be reduced.
  • the discharge rate of the hydraulic pump is less than the sum of the flow rate required to drive the work machine and the flow rate required to drive the cooling fan.
  • the necessary flow rate is preferentially supplied to the work machine, and the remaining flow rate is supplied to the cooling fan drive, so that the work efficiency of the work machine can be reduced. Therefore, it is particularly preferable for a work vehicle such as a bulldozer or the like that has a short working machine operation time because the cooling capacity of the cooling fan is not greatly reduced.
  • a bulldozer 1 to which the present invention is applied includes a pair of left and right crawler type traveling devices 3, 3 at the lower part of a body frame 2, and an upper rear side of the body frame 2. Is equipped with an operation room 4.
  • the engine 19 and a cooling device 17 such as a radiator and an oil cooler are provided at the inner front of the vehicle body frame 2, and a cooling fan 18 is provided in the vicinity of the cooling device 17 on the leeward side of the cooling air.
  • the cooling fan 18 is driven to rotate by the hydraulic motor 10.
  • the U-shaped work implement support frame 6 in a top view is attached so that the opening side thereof is directed to the rear of the vehicle, and end portions on the opening side are swingable up and down on the left and right sides of the body frame 2. Then, the blade 5 tilts back and forth around the vertical axis through the universal connection portion 6a to the front end portion of the front projecting portion 6e formed on the front left side of the work equipment support frame 6 facing the front of the vehicle. (Hereafter, Angle
  • tilt Freely and tilted left and right (hereinafter referred to as tilt) around the longitudinal axis.
  • a pair of left and right lift cylinders 7 and 7 are mounted between the left and right upper surface portions on the opening side of the work implement support frame 6 and the left and right side portions of the vehicle body frame 2 to drive the work implement support frame 6 up and down.
  • An angle cylinder 8 that drives the blade 5 at an angle is attached between the front projecting portion 6 e of the work machine support frame 6 and the right end portion of the back surface of the blade 5.
  • the bracket 6b provided on the upper part of the forward projecting portion 6e of the work implement support frame 6 and the blade 5 are connected by a link 6c via a self-connecting portion 6d located above the universal connecting portion 6a. It has been.
  • FIG. 1 is a block diagram of a hydraulic circuit of a bulldozer according to an embodiment.
  • the hydraulic motor 10, which is a cooling fan driving actuator, is controlled in its flow rate and direction by a direction switching valve 13.
  • the working fluid actuators of the lift cylinders 7 and 7, the tilt cylinder 9 and the angle cylinder 8 are controlled by the direction switching valves 14, 15 and 16, respectively.
  • These directional control valves 1 3, 14, 15 and 16 are composed of pilot operated directional control valves.
  • the electromagnetic pilot operation valves 21a and 21b are configured to input a control signal from the controller 20 to the solenoid portion and output a pilot pressure corresponding to the magnitude of the control signal.
  • the output pilot pressure of the electromagnetic pilot operation valves 21a and 21b is input to the pilot operation portion of the direction switching valve 13 through the pilot pipe lines 31a and 31b.
  • pilot operation valves 22a, 22b, 23a, 23b, 24a, 24bi3 ⁇ 4 which output pilot pressure according to the operation amount of the lift operation Reno 41, Chino re operation 42, and the angle operation lever 43, respectively.
  • the pilot valves 32a, 32b, 33a, 33b, 34a, 34b are connected to the pilot operating portions of the direction switching valves 14, 15, 16, respectively.
  • norot pipes 32a, 32b, 33a, 33b, 34a, 34b are provided.
  • Pressure sensors 25a, 25b, 26a, 26b, 27a, 27b are provided for detecting the norot pressure.
  • the detection signals from these pressure sensors 25a, 25b, 26a, 26b, 27a, and 27b are input to the controller 20 as operation amount signals for the lift operation lever 41, tilt operation lever 42, and angle operation lever 43, respectively.
  • the swash plate angle (corresponding to the discharge amount) of the hydraulic pump 11 is set to each direction switching valve 13,. It is a so-called load sensing circuit that is controlled according to the opening amount (ie, required flow rate) of 14, 15, 1 6 (however, the load sensing circuit is not shown in detail in the block diagram of FIG. 1) .)
  • the swash plate angle of the hydraulic pump 11 is set so that the differential pressure between the pump discharge pressure and the load pressure (differential pressure before and after each directional control valve 13, 14, 15, 16) is the same regardless of the load pressure.
  • the swash plate drive cylinder 12a to be adjusted is controlled. Opening force of each directional control valve 13, 14, 15, 16 Otherwise, only a small flow rate is required to generate the same differential pressure. Conversely, if the opening is large, the same differential pressure is generated. It requires a large flow rate to make it happen. Therefore, on Road
  • the swash plate angle of the hydraulic pump 11 is automatically adjusted so that the flow rate corresponding to the opening amount of each direction switching valve 13, 14, 15, 16 is always discharged.
  • the control of the swash plate angle of the hydraulic pump 11 by port sensing is a force that can use a method such as a hydraulic servo, an electric servo, an electric hydraulic servo, etc. Since these techniques are well known, a detailed description is omitted. .
  • the entire configuration including each hydraulic device such as the hydraulic servo, electric servo, and electrohydraulic servo for controlling the hydraulic circuit and the controller 20 is referred to as a control device 50.
  • the hydraulic pump 11 has a maximum discharge amount Qmax force, a maximum flow rate Q Wmax required for driving the work machine (when the operation amounts of the lift operation lever 41, the tilt operation lever 42, and the angle operation lever 43 are all maximum).
  • the controller 20 is composed of, for example, a computing device such as a microcomputer, and the detection signals of the pressure sensors 25a, 25b, 26a, 26b, 27a, 27b, that is, the lift operation lever 41, the tilt operation lever 42, and the angle Based on the operation amount of the operation lever 43, the supply flow rate to the work machine actuators of the lift cylinders 7, 7, the tilt cylinder 9 and the angle cylinder 8 is obtained, and the total flow rate required to drive the work machine (hereinafter referred to as the work machine flow rate). ) Calculate QW by calculation.
  • a computing device such as a microcomputer
  • the controller 20 stores the detected pressure values of the pressure sensors 25a, 25b, 26a, 26b, 27a, 27b and the flow rates supplied to the diff cylinder 7, 7, the chino cylinder 9, and the angle cylinder 8 in the storage device.
  • the controller 20 inputs the engine water temperature, the hydraulic oil temperature, and the engine speed detected by the engine water temperature sensor 36, the hydraulic oil temperature sensor 37, and the engine speed sensor 38, respectively, and according to these input values.
  • the target rotational speed of the cooling fan 18 is obtained by calculation so that the engine water temperature and hydraulic oil temperature are below the allowable values, and the flow rate to the hydraulic motor 10 corresponding to the target rotational speed (hereinafter referred to as fan flow rate).
  • Fan flow rate the flow rate to the hydraulic motor 10 corresponding to the target rotational speed
  • the total flow rate of the machine flow rate QW and fan flow rate QF is compared with the preset maximum discharge rate Qmax of the hydraulic pump 11, and based on the comparison result! /,
  • the electromagnetic performance is as follows.
  • a control signal is output to the pilot operation valves 21a and 21b to control the opening amount of the direction switching valve 13, that is, the fan flow rate.
  • the controller 20 controls the opening amount of the direction switching valve 13 via the electromagnetic pilot operation valves 21a and 21b so as to supply the obtained fan flow rate QF to the hydraulic motor 10.
  • the controller 20 sets the fan flow rate as "Qmax- “QW” is obtained by calculation, and the opening amount of the direction switching valve 13 is controlled via the electromagnetic pilot operated valves 21a and 2 lb so as to supply the hydraulic motor 10 with a flow rate equal to “Qmax ⁇ QW”.
  • the supply of the work machine flow rate QW is prioritized, and the cooling fan 18 rotates at a rotation speed corresponding to the flow rate “Qmax—QW” smaller than the required fan flow rate QF.
  • the opening amounts of the direction switching valves 14, 15, and 16 for driving the work machine actuator are respectively determined by the pilot operation valves 22a, 22b, Since the pressure is automatically adjusted according to the operation pilot pressures 23a, 23b, 24a, and 24b, the work implement flow rate QW is always supplied to the work implement.
  • the discharge volume of the variable displacement hydraulic pump 11 is automatically controlled to discharge a flow rate corresponding to the opening amount of the directional control valves 13, 14, 15, 16 for driving the cooling fan and driving the work equipment. Yes.
  • the discharge amount of the variable displacement hydraulic pump 11 is only the fan flow rate, so that the loss can be extremely reduced and the efficiency can be improved.
  • the controller 20 Priority is given to the supply of W, and the opening amount of the direction switching valve 13 for driving the cooling fan is controlled so that the fan flow rate becomes “Qmax-QW”.
  • the work machine drive is given priority, and the number of rotations of the cooling fan 18 is reduced. Therefore, even if the flow for driving the cooling fan is temporarily reduced, the influence on the overall cooling capacity is small.
  • the variable displacement hydraulic pump 11 has its maximum discharge amount Qmax force. The maximum flow rate QWmax required to drive the work implement and the maximum flow rate QFmax required to drive the cooling fan 18 at the maximum rotation speed Therefore, a small hydraulic pump can be used.
  • the present invention is not limited to this, and the work implement operating lever is configured with an electric lever. Even if the controller 20 inputs the operation amount signal to the controller 20, and the controller 20 outputs a command to the electromagnetic pilot operation valve in accordance with the operation amount signal to control the direction switching valve for driving the work implement, The present invention is applicable.
  • the work implement flow rate QW is calculated by calculation based on the pilot pressure of each work implement operation, but each work implement operation lever 41, 42, 43 (including the case of the electric lever described above). Let's calculate it based on the operation stroke.
  • the hydraulic pump 11 is not limited to be driven to rotate by an engine, and may be configured to be driven to rotate by an electric motor.
  • the present invention is not limited to a bulldozer but can be applied to a wheel loader and other work vehicles.
  • FIG. 1 is a block diagram of a hydraulic circuit according to an embodiment.
  • FIG. 2 is a side view of a bulldozer to which the present invention is applied.
  • FIG. 3 is a plan view of a bulldozer to which the present invention is applied. Explanation of symbols

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

Circuit hydraulique pour un véhicule de travail, augmentant le rendement et approprié pour actionner un ventilateur et une machine de travail. Le circuit a un actionneur de machine de travail, un actionneur pour actionner le ventilateur, une pompe hydraulique commune à cylindrée variable pour fournir de l’huile pressurisée à l’actionneur de la machine de travail et à l’actionneur pour actionner le ventilateur, et un dispositif de contrôle pour contrôler le débit de l’huile pressurisée fournie à l’actionneur de la machine de travail et le débit de l’huile pressurisée fournie à l’actionneur pour actionner le ventilateur. La capacité de refoulement maximale de la pompe hydraulique à cylindrée variable est inférieure à la somme du débit maximal requis pour actionner la machine de travail et du débit maximal requis pour actionner le ventilateur. Quand le débit de la pompe hydraulique est inférieur à la somme du débit maximal requis pour actionner la machine de travail et du débit maximal requis pour actionner le ventilateur, le dispositif de contrôle délivre le débit requis pour actionner la machine de travail et le débit restant à l’actionneur pour actionner le ventilateur. SCHÉMAS: FIGURE 1: UN SCHÉMA FONCTIONNEL DU CIRCUIT HYDRAULIQUE RELATIF AU MODE DE FONCTIONNEMENT DU CONTRÔLEUR 20 DE L’INVENTION
PCT/JP2005/010062 2004-06-01 2005-06-01 Circuit hydraulique pour véhicule de travail Ceased WO2006008875A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2004-162676 2004-06-01
JP2004162676A JP2005344766A (ja) 2004-06-01 2004-06-01 作業車両の油圧回路

Publications (1)

Publication Number Publication Date
WO2006008875A1 true WO2006008875A1 (fr) 2006-01-26

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PCT/JP2005/010062 Ceased WO2006008875A1 (fr) 2004-06-01 2005-06-01 Circuit hydraulique pour véhicule de travail

Country Status (2)

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JP (1) JP2005344766A (fr)
WO (1) WO2006008875A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101506484B (zh) * 2006-08-24 2011-05-25 株式会社小松制作所 风扇驱动系统
WO2020059130A1 (fr) * 2018-09-21 2020-03-26 日立建機株式会社 Dispositif de commande de ventilateur à entraînement hydraulique

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7257132B2 (ja) * 2018-11-15 2023-04-13 株式会社小松製作所 作業機械
JP2023117580A (ja) * 2022-02-14 2023-08-24 コベルコ建機株式会社 油圧駆動装置及びこれを備えた建設機械
WO2024048527A1 (fr) * 2022-08-29 2024-03-07 日立建機株式会社 Véhicule de transport

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3664129A (en) * 1968-05-08 1972-05-23 Hyster Co Hydraulic cooling system
JP2001003385A (ja) * 1999-05-04 2001-01-09 Caterpillar Inc 機械のパワー制御システム
JP2004508480A (ja) * 2000-09-08 2004-03-18 テレックス　ジャーマニー　ゲゼルシャフト　ミット　ベシュレンクテル　ハフツング　ウント　コンパニー　コマンディートゲゼルシャフト 建設機械および／または作業機械における内燃機関のファン駆動装置を制御するための方法および装置
JP2004239389A (ja) * 2003-02-07 2004-08-26 Shin Caterpillar Mitsubishi Ltd オイルクーラ制御方法およびオイルクーラ制御装置
JP2004316814A (ja) * 2003-04-17 2004-11-11 Shin Caterpillar Mitsubishi Ltd 液体粘度制御方法および液体粘度制御装置

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3664129A (en) * 1968-05-08 1972-05-23 Hyster Co Hydraulic cooling system
JP2001003385A (ja) * 1999-05-04 2001-01-09 Caterpillar Inc 機械のパワー制御システム
JP2004508480A (ja) * 2000-09-08 2004-03-18 テレックス　ジャーマニー　ゲゼルシャフト　ミット　ベシュレンクテル　ハフツング　ウント　コンパニー　コマンディートゲゼルシャフト 建設機械および／または作業機械における内燃機関のファン駆動装置を制御するための方法および装置
JP2004239389A (ja) * 2003-02-07 2004-08-26 Shin Caterpillar Mitsubishi Ltd オイルクーラ制御方法およびオイルクーラ制御装置
JP2004316814A (ja) * 2003-04-17 2004-11-11 Shin Caterpillar Mitsubishi Ltd 液体粘度制御方法および液体粘度制御装置

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101506484B (zh) * 2006-08-24 2011-05-25 株式会社小松制作所 风扇驱动系统
WO2020059130A1 (fr) * 2018-09-21 2020-03-26 日立建機株式会社 Dispositif de commande de ventilateur à entraînement hydraulique
JPWO2020059130A1 (ja) * 2018-09-21 2020-12-17 日立建機株式会社 油圧駆動ファン制御装置
US11396839B2 (en) 2018-09-21 2022-07-26 Hitachi Construction Machinery Co., Ltd. Hydraulic drive fan control device

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